WO2012139833A1 - Dispositif d'entraînement comportant au moins un moteur électrique - Google Patents

Dispositif d'entraînement comportant au moins un moteur électrique Download PDF

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Publication number
WO2012139833A1
WO2012139833A1 PCT/EP2012/054212 EP2012054212W WO2012139833A1 WO 2012139833 A1 WO2012139833 A1 WO 2012139833A1 EP 2012054212 W EP2012054212 W EP 2012054212W WO 2012139833 A1 WO2012139833 A1 WO 2012139833A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive
gear
shaft
planetary
axis
Prior art date
Application number
PCT/EP2012/054212
Other languages
German (de)
English (en)
Inventor
Tomas Smetana
Philip Wurzberger
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to US14/111,424 priority Critical patent/US8974341B2/en
Priority to CN201280017989.6A priority patent/CN103635339B/zh
Publication of WO2012139833A1 publication Critical patent/WO2012139833A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
    • B60W10/11—Stepped gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/12—Conjoint control of vehicle sub-units of different type or different function including control of differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/112—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches in combination with brakes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
    • H02K2213/09—Machines characterised by the presence of elements which are subject to variation, e.g. adjustable bearings, reconfigurable windings, variable pitch ventilators

Definitions

  • the invention relates to a drive device with at least one electric machine, with a manual transmission, with a by the electric machine via the gearbox driven differential, with at least one torque-fixed first operative connection between a first drive shaft of the electric machine and the manual transmission.
  • DE 10 2005 022 926 B3 shows a drive device with at least one electric machine, with a manual transmission and with a differential.
  • the electric machine has a drive shaft rotatable about a drive rotation axis.
  • the drive shaft is operatively connected to a coaxial transmission shaft of the two-speed gearbox torque-resistant.
  • On the gear shaft sits a drive gear, which is rotatably driven by the drive shaft about the axis of rotation of the electric machine.
  • the drive gear meshes with an idler gear that sits on an intermediate shaft.
  • the intermediate shaft receives two idler gears, which are rotatable relative to the intermediate shaft about the intermediate shaft rotation axis.
  • a clutch is formed by a variable converter, a sliding sleeve and coupling elements on the loose wheels.
  • linearly movable sliding sleeve is an engageable and disengageable operative connection between the electric machine and optionally produced with the coupling teeth of one or the other of the idler gears.
  • the mechanically operated mechanical variable converter has an input member in the form of a roller and an output member in the form of a shift finger.
  • the operative connection between the roller rotatable about its own rotation axis and the shift finger is formed by a circumferentially encircling guide track which deflects in the longitudinal direction and into which the shift finger engages.
  • the shift finger travels along the guide track and is moved longitudinally in accordance with the deflection of the guide track. This causes the sliding sleeve selectively engages with a coupling teeth in one of the coupling teeth of one of the idler gears or disengaged from this.
  • the idler gear is rotationally fixed to the intermediate shaft and can accordingly rotate with the intermediate shaft about the intermediate shaft rotation axis.
  • Each idler gear is in meshing engagement with an input gear of the differential, which is fixed rotationally fixed on the differential cage, so that an operative connection between the transmission and the differential is made.
  • the differential is a classic bevel gear differential that distributes torques from the differential cage via bevel gears to axle bevel gears of left and right axleshafts.
  • the axle shafts are connected to driven wheels of a vehicle, but can also lead to driven axles when the differential is used in a transfer case.
  • the input gears are concentric with the central axes of the axle bevel gears.
  • the axial distances of the spaced apart axis-parallel drive rotation axis to the intermediate shaft rotation axis and to the central axes are dependent on the ratios of the gear stages and the size of the torques to be transmitted.
  • the space required accordingly by the drive device can be disadvantageously large.
  • the object of the invention is to provide a variable drive device which is easy to assemble and which is compact.
  • the object is solved by the subject matter of claim 1.
  • a clutch of a second operative connection is provided directly between the first drive shaft and the gearbox in addition to a torque-first first operative connection between the drive shaft of the electric machine, wherein the clutch is aligned coaxially with the electric machine.
  • Coaxial alignment of the clutch is called that substantially all rotationally symmetric elements of the clutch, such as friction plates or friction cones or claw rings are arranged concentrically to the first axis of rotation.
  • the input and release device has an actuator with a second drive shaft, which is at least pivotable or rotatable about an axis.
  • the axis of the second drive shaft is aligned axially parallel to the first axis of rotation.
  • Axially parallel means either that the axis of the drive shaft of the actuator is located on the first axis of rotation or is aligned parallel to this at a distance.
  • the first operative connection between the drive shaft of the electric machine and the gearbox is, for example, a torque-transmitting (torque-resistant, torque-resistant) plug-in or flange connection, preferably between the drive shaft and a connection shaft of a planetary drive of the gearbox provided according to an embodiment of the invention.
  • the connecting shaft is, for example, a sun gear of the planetary drive.
  • connection shafts or connected shafts of planetary gears the expert understands drive shafts, output shafts and also referred to as reaction members fixed links.
  • Such connection shafts may be: sun gears also referred to as central wheels, planet carriers and ring gears also referred to as webs [see “gear transmission” J. Loomann, third extended edition of 1996, chapter 3.1 Definitions and terms]
  • the second operative connection is an engageable and disengageable operative connection between the drive shaft of the electric machine and a connecting shaft of the planetary drive, for example a clutch between a shaft or a shaft of the sun gear.
  • the operative connection is a clutch between the drive shaft of the electric machine and another connecting shaft of the planetary drive, for example between the drive shaft and a ring gear of the planetary drive. Since the drive shaft and the sun gear are rotatably connected to each other, the clutch is an engageable and disengageable operative connection between the sun gear and the ring gear of the planetary gear.
  • Coupling members for connecting the two connecting shafts are, for example, friction disks, friction cones and jaws of jaw clutches.
  • the advantage of the invention is that by engaging or disengaging the clutch and thus by connecting or disconnecting the drive shaft and gearbox, at least two different operating conditions (gears) of the multi-speed planetary gear can be switched while little space is required for the switching device.
  • the elements of the electric machine and the clutch are arranged side by side along the main axis of the drive device or surround each other.
  • the first connecting shaft is a sun gear, which meshes with at least one set of planetary gears.
  • the second connecting shaft is a planetary carrier on which the planet gears are rotatable about their own axes of rotation, for example, on planet pins, stored.
  • the third connecting shaft is a ring gear, with the internal teeth of the planetary gears are in meshing engagement.
  • the clutch disengaged and the ring gear for example, with respect to the environment, for example, with respect to a housing of the drive device, held the drive shaft of the electric machine drives the sun gear, which sets the planetary gears in rotation, wherein the planet gears are supported on the teeth of the stationary ring gear and set the planet carrier in rotation, thereby driving a connecting shaft of the second planetary differential or the differential.
  • the operative connection between the electromotive drive and the second planetary drive or the differential is determined by an over or reduction ratio of the planetary drive.
  • the third operative connection is formed between the drive shaft of the actuator for the actuation of the clutch and an adjusting converter and is preferably a geared connection.
  • the actuator itself is optionally a linear drive, such as a ball screw drive, which is preferably driven by an electric motor. Alternatively, the actuator is just an electric motor.
  • the torque converter is for example a lever, a shift drum with shift fork or shift finger.
  • the position transducer has a rotatable input member which drives an output member linearly movable.
  • the input member of the variable converter is optionally a link, a drum or a roller on which concentric outer teeth is fixed.
  • the output member of the variable speed converter engages linearly movable on a coupling element of the clutch or a lever and other adjusting means for engaging and disengaging a clutch and has a in the broadest sense a designated as a projection cam, pin or shift finger or a fork on a coupling member, for example, acts on a sliding sleeve.
  • the operative connection between the input member and the output member, with the rotation is converted into a linear movement, for example, prepared by a projection, a shift finger or such engages in a guideway of the input member so that this projection in the guideway forcibly moved along ,
  • the geared connection is, for example, a ring gear with an internal gear or a planet carrier of a planetary drive, when the drive shaft of the drive and the axis of rotation of the drive shaft of the electric machine for the actuation of the clutch are arranged concentrically to one another.
  • the operative connection between the transmission and the differential is preferably formed by a torque transmitting connection between two transmission shafts.
  • One of the transmission shafts for example, a connecting shaft of a planetary gear of the gearbox, which is connected to the differential.
  • This planetary gear may be the first mentioned planetary gear or another (second) planetary gear of the gearbox.
  • the other transmission shaft, that of the differential is, for example, a differential cage of a classic bevel gear differential or a planet carrier of a planetary differential.
  • the gearbox has two planetary gears operatively connected to each other.
  • the first planetary drive and the second planetary drive can in the simplest form each of the three connection waves; Sun gear, planet carrier and ring gear and be formed from a set planetary gears or can have more connecting shafts and more planetary gear sets.
  • the first axis of rotation is the main axis of the drive device, at the same time the axis of rotation of the drive shaft of the electric machine and at the same time central axis of rotation of the respective planetary drive.
  • the electric machine, the planetary gears and the differential are with respect to the axes of rotation arranged coaxially with each other, wherein the axis of rotation of the bevel gear differential coincides with the central axes of the Achswellenlie and thus with the axis of rotation of the differential cage.
  • the axis of rotation of the planetary differential corresponds to that of the sun gears.
  • Torque transmitting connection - Torque resistant; torque-proof - is understood to mean frictional engagement, frictional engagement, form-fitting or magnetic adhesion with which, with or without slip, torques can be transmitted from one of the connecting shafts to the other of the connecting shafts. Examples are serrations, plug connections between shafts, flanges or couplings. Torque-resistant connections are also geared connections such as gear stages or chain and belt drives, clutches are single or multiple discs, wet or dry clutches, claw or magnetic clutches or other suitable couplings. The elements of the clutch such as friction plates or disks, pressure plates, coupling body, etc. are preferably annular and arranged concentrically to the axis of rotation.
  • An embodiment of the invention provides a brake between the third connection shaft, ie between the ring gear, and a housing of the drive device by means of which the connection shaft can be braked and secured relative to the housing.
  • the drive device is designed variable.
  • the third connection shaft can be braked and secured by means of the brake relative to the housing.
  • the brake is a wet or dry disc brake, a band or shoe brake with which the third connection shaft can be braked and fixed directly to the housing or indirectly to supports rotatably connected to the housing relative to the housing of the drive device.
  • the brake is like the clutch also mechanically operated or alternatively operated with pressure medium.
  • the controls can be like the be designed and arranged the clutch.
  • the operation of the brake as an embodiment of the invention provides, with the input and Ausgurvorraumiques for the clutch can be inserted and released again. If the clutch is disengaged, the transmission can remain in a neutral position or the brake is engaged. When the brake is released, the transmission can remain in the neutral position or the clutch is engaged.
  • a further embodiment of the invention provides an overrunning clutch in the manual transmission.
  • the overrunning clutch sits between the housing and the ring gear. When releasing the brake, the ring gear continues to support the blocked freewheel immobile as long as the case until the clutch is engaged and starts an overtaking freewheeling. Thus, the duration of the traction interruption can be reduced when upshifting.
  • FIG. 1 schematically shows a longitudinal section through an exemplary embodiment of a drive device 1.
  • the drive device 1 has an electric machine 2, a clutch 13 (K1), a brake 12 (B1) an actuator 1 1, a transmission in the form of a two-speed planetary gear 20 and a differential 5.
  • the actuating device 1 1 is formed from an actuator 23, a geared connection 25, a geared connection 26 and an adjustable converter 24.
  • the electric machine 2, the clutch 13 and the brake 1 2, the two-speed planetary gear 20 and the differential 5 are arranged coaxially to each other and have as common main axis the axis of rotation 10, or an axial extension of this, the rotor shaft 9 and thus the drive shaft 9 'up.
  • the axis 23a of the actuator which may be a rotation axis or a pivot axis, is arranged at a distance axially parallel to the rotation axis 10.
  • the electric machine 2 is accommodated in a housing section of a housing 6, not completely shown in FIG. 1 and composed of housing sections, of the drive device 1 and has a rotor 7, a stator 8 and the rotor shaft 9.
  • the rotor 8 is seated at least rotationally fixed in the housing 6.
  • the rotor 7 is concentric at least rotationally fixed on the rotor shaft 9.
  • the rotor shaft 9 is rotatable with the rotor 7 about the rotation axis 10 relative to the stator 8
  • the two-speed planetary gear 20 has a first planetary gear 3 and a second planetary gear 4.
  • the rotor shaft 9 is drive shaft 9 of the electric machine is operatively connected to the first planetary gear 3 via a first connection shaft 1 5.
  • the first connection shaft 15 of the first planetary drive 3 is a rotatable about the rotation axis 10 sun gear 3a, which is either integrally formed with the drive shaft 9 or formed as a separate component and rotatably connected thereto at least about the rotation axis 10 relative to this torque.
  • the first planetary drive 3 is operatively connected to the second planetary gear 4 via the second connecting shaft 16 and a third connecting shaft 17.
  • the third connecting shaft 17 is a rotatable about the rotation axis 10 sun gear 4a of the second planetary drive 4.
  • the second connecting shaft 16 and the third connecting shaft 17 are formed either integrally with each other or at least torque-resistant connected as each separately formed components.
  • the two-speed planetary gear 20 is operatively connected to the differential 5 via a fourth connecting shaft 18 and a fifth connecting shaft 19.
  • the fourth connecting shaft 18 is a planetary carrier 4b of the second planetary drive 4 which is rotatable about the axis of rotation 10.
  • the fifth connecting shaft 19 is a differential cage 5a of the differential 5 and is thus the sum shaft 19 'of the differential 5. Since the differential 5 is a planetary differential 5', is the differential cage 5a of the planet carrier 5a 'of the planetary differential 5'.
  • the planetary differential 5 ' is operatively connected via a sun gear 5d' to an output shaft 21 and via a sun gear 5e 'to an output shaft 22.
  • the independently rotatable about the axis of rotation output shafts 21 and 22 lead to unillustrated driven wheels or each to a driven shaft of a vehicle.
  • the first planetary drive 3 is shown enlarged in a section of Figure 1.
  • the first planetary drive 3 is formed from the sun gear 3a, from the planet carrier 3b, from a set of planetary gears 3c, of which only one planetary gear 3c is shown, and from a ring gear 3d.
  • the planet carrier 3b and the ring gear 3d are mounted rotatably about the rotation axis 10 in the drive device 1.
  • the planet gears 3c are rotatably mounted on planet pins on the planet carrier 3b and are in meshing engagement with the sun gear 3a and the ring gear 3d.
  • the second planetary gear 4 is shown enlarged in a section of Figure 1.
  • the second planetary gear 4 is formed from the sun gear 4a, the planet carrier 4b, from a set of planetary gears 4c, of which only one planetary gear is shown, and from a ring gear 4d.
  • the planet gears 4c are rotatably mounted on planet pins 4b on the planet carrier and are in meshing engagement with the sun gear 4a and the ring gear 4d.
  • the planet carrier 4b is mounted rotatably about the rotation axis 10 in the drive device.
  • the ring gear 4d is held stationary on the housing 6.
  • the planetary differential 5 ' is shown enlarged in a detail of Figure 1.
  • the planetary differential 5 ' is formed from the planet carrier 5a, from two sets of differential gears 5b and 5c in the form of planets 5b' and 5c 'and from the output wheels 5d and 5e in the form of the sun gears 5d' and 5e '.
  • the planet gears 5b 'of the one planetary gear set are in meshing engagement with the sun gear 5d' and the planet 5c 'with the sun gear 5e'.
  • Both sets planet 5b 'and 5c' are rotatably mounted on planet pins on the planet carrier 5a '.
  • the sun wheels 5cT and 5e ' are rotationally fixed to the output shafts 12 and 22, respectively.
  • the clutch 13 has a cone 13a, on which a friction surface 13b is formed.
  • the clutch 13 is provided with a coupling member (27 ') in the form of a sliding sleeve 27, which is associated with a friction surface 13c fixed torque.
  • the friction surface 13c is conical and corresponds with respect to the geometry and the friction behavior with the friction surface 13b and is axially opposite.
  • the cone 13 a, the friction surfaces 13 b and 13 c and the sliding sleeve 27 are arranged concentrically to the axis of rotation 10.
  • the cone 13a is coupled to the drive shaft 9 torque-tight.
  • the brake 12 has a cone 12a, on which a conical friction surface 12b is formed.
  • the friction surface 12b is opposite to the sliding sleeve 27 associated friction surface 12c, which corresponds with respect to geometry and friction with the friction surface 12b.
  • the cone 12 a and the friction surfaces 12 b and 12 c are aligned concentrically with the axis of rotation 10.
  • the cone 12a is torque-resistant with respect to the environment, that is to say with respect to the housing 6.
  • the friction surface 12b is associated torque-tight with the cone 12a.
  • the sliding sleeve 27 is torque-fixed but longitudinally along the axis of rotation 10 slidably connected to a fifth connecting shaft 28 which is the ring gear 3d of the first planetary gear 3.
  • the ring-shaped sliding sleeve 27 has the outer peripheral side an annular groove 27a, in which a shift finger 24a of the converter 24 engages.
  • the shift finger 24a is supported in the annular groove 27a by means of a thrust bearing 29 which acts twice in both longitudinal directions of the axis of rotation 10.
  • the thrust bearing 29 may alternatively be a radial ball bearing, a double row angular contact ball bearing or a four-point bearing.
  • the actuator 23 of the input and release device 1 1 is an electric machine and has as a drive shaft 23b, the rotor shaft of the electric motor. With the drive shaft 23b, a gear 26a of the geared connection 26 is connected torque-tight. The gear 26a is in meshing engagement with another gear 26b of the geared connection, which sits firmly on an intermediate shaft 1 1 a.
  • the intermediate shaft 1 1 is a torque-fixed connection between the gear 26b and a gear 25a of the geared connection 25 and is aligned at a distance axially parallel to the axis of rotation 10, but may alternatively be aligned transversely to this.
  • the gears are bevel gears, while the gears 26a, 26b, 25a and 25b are spur gears.
  • the gear 25a is in meshing engagement with the gear 25b, which sits fixed torque on the outer circumference of a roller 24b of the converter 24.
  • the roller 24b is aligned concentrically with the axis of rotation 10 and has a guideway 24c, which extends substantially circumferentially of the roller 24b, but in the longitudinal directions, that is deflected in the same direction to the axis of rotation 10 is curved
  • the actuator 23 is driven.
  • the drive shaft 23a pivots or rotates and drives the roller 24b via the geared connections 26 and 25, which thereby pivots or rotates about the rotation axis 10.
  • the guideway 24c moves relative to the shift finger 24a, which is forcibly moved along the curved path of the guideway 24a longitudinally and entrains the sliding sleeve 27 in the longitudinal direction.
  • a first gear is engaged, in which the friction surfaces 1 2b and 12c are brought into frictional engagement with each other and the ring gear 3d is thereby held against the housing 6.
  • the sun gear 3a which rotates the planet gears 3c about its own axis of rotation.
  • the planet gears 3c are based on the internal toothing of the ring gear 3d and run at a radial distance around the rotation axis, so that the planetary carrier 3b is rotated about the rotation axis 10 and thereby drives the sun gear 4a.
  • a second gear is switched, in which the friction surfaces 1 3b and 1 3c are brought into frictional contact with each other.
  • the sun gear 3a and the ring gear 3d are connected to each other fixed torque. Since the sun gear 3a and the ring gear 3d can no longer rotate relative to each other, the effect of the first planetary gear 3 is canceled.
  • the drive shaft 9 drives the sun gear 3a and the ring gear 3d in the same direction of rotation about the axis of rotation 10, whereby the planet carrier 3b is taken and drives the sun gear 4a.
  • FIG. 2 shows a drive device 30 which basically has the same design and functions like the drive device 1 according to FIG. 1.
  • the drive device 30 additionally has a freewheel 14 (F1), which is arranged concentrically to the rotation axis 10 next to the brake 12 and is supported torque-proof on the outside relative to the housing 6.
  • the freewheel 14 is torque-tight on the fifth connecting shaft 28.
  • the freewheel 14 blocked when upshifting from the first gear to the second gear until the friction surfaces 13b and 13c make frictional contact with each other.
  • the freewheel 14 runs free when frictional contact between the friction surfaces 1 3b and 1 3c.
  • FIG. 3 shows a drive device 31 into which drive power can be introduced into the drive device 31 independently of one another or cooperatively with two drives.
  • One of the drives is the electric machine 2, the other drive may be an internal combustion engine or another electric machine.
  • the drive power of the latter and not shown in Figure 3 drive is introduced via an angle drive 32 in the drive device 31.
  • Angular drive 32 has a pinion shaft 32a, which is rotatably mounted about its own axis of rotation 32b, for example in the housing 6.
  • the rotation axis 32b is directed transversely to the rotation axis 10.
  • On the pinion shaft 32a sits a fixed torque pinion 32c, which is in mesh with a ring gear 32d.
  • the ring gear 32d is optionally fixed torque on the planet carrier 4b or on the planet carrier 5a '.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne un dispositif d'entraînement (1, 30, 31) comportant au moins un moteur électrique (2), une boîte de vitesses, un différentiel (5) pouvant être entraîné par le moteur électrique par l'intermédiaire de la boîte de vitesses, au moins une première liaison active à couple fixe entre un premier arbre d'entraînement (9') du moteur électrique et la boîte de vitesses.
PCT/EP2012/054212 2011-04-13 2012-03-12 Dispositif d'entraînement comportant au moins un moteur électrique WO2012139833A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US14/111,424 US8974341B2 (en) 2011-04-13 2012-03-12 Drive device with at least one electric engine
CN201280017989.6A CN103635339B (zh) 2011-04-13 2012-03-12 具有至少一个电机的驱动设备

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011007260.8 2011-04-13
DE102011007260A DE102011007260A1 (de) 2011-04-13 2011-04-13 Antriebsvorrichtung mit wenigstens einer elektrischen Maschine

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Publication Number Publication Date
WO2012139833A1 true WO2012139833A1 (fr) 2012-10-18

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PCT/EP2012/054212 WO2012139833A1 (fr) 2011-04-13 2012-03-12 Dispositif d'entraînement comportant au moins un moteur électrique

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US (1) US8974341B2 (fr)
CN (1) CN103635339B (fr)
DE (1) DE102011007260A1 (fr)
WO (1) WO2012139833A1 (fr)

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WO2013178457A1 (fr) * 2012-05-29 2013-12-05 Schaeffler Technologies AG & Co. KG Dispositif d'entraînement pour un véhicule
CN104981366A (zh) * 2012-12-17 2015-10-14 大众汽车有限公司 变速和差速传动装置以及发动机和传动装置单元
WO2016086930A1 (fr) * 2014-12-03 2016-06-09 Schaeffler Technologies AG & Co. KG Boîte de vitesses à roues planétaires
US9841091B2 (en) 2012-06-14 2017-12-12 Volkswagen Aktiengesellschaft Speed-changing and differential transmission and motor and transmission unit

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DE102011007454B4 (de) 2011-04-15 2022-06-15 Schaeffler Technologies AG & Co. KG Elektrische Achsantriebsvorrichtung mit zwei Untersetzungsstufen
DE102012201376A1 (de) * 2012-01-31 2013-08-01 Zf Friedrichshafen Ag Hybridantriebsstrang für ein Kraftfahrzeug
JP6324323B2 (ja) * 2012-03-15 2018-05-16 ボルグワーナー スウェーデン エービー 道路車両のための電気的駆動軸装置
DE102012208926B4 (de) * 2012-05-29 2020-03-12 Schaeffler Technologies AG & Co. KG Elektroachse für ein Fahrzeug
DE102012024752A1 (de) * 2012-12-17 2014-06-18 Volkswagen Aktiengesellschaft Übersetzungs- und Ausgleichsgetriebe sowie Motor- und Getriebeeinheit
DE102014220347B4 (de) 2014-10-08 2022-06-02 Zf Friedrichshafen Ag Getriebeanordnung
DE102015223130B4 (de) * 2015-11-24 2020-02-06 Schaeffler Technologies AG & Co. KG Antriebseinrichtung mit einem Differentialgetriebe und einer Torque-Vectoring-Einheit
DE102015120818B4 (de) * 2015-12-01 2023-03-30 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Getriebe mit schaltbarem Planetensatz sowie Freilaufkupplung für ein elektrisch antreibbares Kraftfahrzeug
CN106627075A (zh) * 2016-11-03 2017-05-10 中国汽车工程研究院股份有限公司 一种适用于电动车的同轴式电驱动桥
DE102017104019B3 (de) 2017-02-27 2018-03-15 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug
DE102017107803B3 (de) 2017-04-11 2018-06-21 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug
DE102017214916B4 (de) * 2017-08-25 2021-10-07 Audi Ag Differentialgetriebeeinrichtung mit schaltbarer Torque Vectoring-Funktionalität
US11280391B2 (en) * 2018-09-25 2022-03-22 Dana Automotive Systems Group, Llc Multi-speed gearbox and the drive axle made therewith
DE102019205747A1 (de) * 2019-04-23 2020-10-29 Zf Friedrichshafen Ag Getriebe und Antriebsstrang und Fahrzeug
DE102019210779A1 (de) * 2019-07-19 2021-01-21 Magna powertrain gmbh & co kg Elektrisches Antriebssystem und Verfahren zum Betrieb des Antriebssystems
DE102020123172A1 (de) 2020-09-04 2022-03-10 Schaeffler Technologies AG & Co. KG Getriebeanordnung und elektrisch betreibbarer Antriebsstrang eines Kraftfahrzeugs
DE102021120777A1 (de) 2020-09-11 2022-03-17 Schaeffler Technologies AG & Co. KG Getriebeanordnung
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WO2013178457A1 (fr) * 2012-05-29 2013-12-05 Schaeffler Technologies AG & Co. KG Dispositif d'entraînement pour un véhicule
US9302580B2 (en) 2012-05-29 2016-04-05 Schaeffler Technologies Gmbh & Co. Kg Drive device for a vehicle
US9841091B2 (en) 2012-06-14 2017-12-12 Volkswagen Aktiengesellschaft Speed-changing and differential transmission and motor and transmission unit
CN104981366A (zh) * 2012-12-17 2015-10-14 大众汽车有限公司 变速和差速传动装置以及发动机和传动装置单元
US9777816B2 (en) 2012-12-17 2017-10-03 Volkswagen Aktiengesellschaft Transmission and differential gearing and engine and gearing unit
WO2016086930A1 (fr) * 2014-12-03 2016-06-09 Schaeffler Technologies AG & Co. KG Boîte de vitesses à roues planétaires

Also Published As

Publication number Publication date
DE102011007260A1 (de) 2012-10-18
US20140106930A1 (en) 2014-04-17
CN103635339A (zh) 2014-03-12
CN103635339B (zh) 2016-10-19
US8974341B2 (en) 2015-03-10

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